Casing capsule ring arrangement for a rotary vane machine



CASING CAPSULE RING ARRANGEMENT FOR A ROTARY vANE MACHINE Filed sept. 2,`.19eo

K. EICKMANN Nov. 26, 1963 2 Sheets-Sheet 1 m mw- INVENTOR KARL EIC/(MANN K. EICKMANN 3,111,905

CASING CAPSULE RING ARRANGEMENT FOR A ROTARY VANE MACHINE Nov. 26, 1963 2 SheetseSheei 2 Filed Sept. 2, 1960 INVENT OR KARL E/c/cMA/VN.

DMZ'ATRN s United States Patent Oli ice 3,1 l 1,905 Patented Nov. 26, 1963 3,111,905 CASWG CAPSULE G ARMNGENENT FOR A RUTARY VA'NE MACHINE Karl Eichmann, 2420 Isshiki, Hayama-machi Miuragun, Kanagawa-ken, Japan Filed Sept. 2, 1960, Ser. No. 53,778 15 Claims. (Cl. 10S- 121) The present invention relates to a casing capsule ring arrangement for rotary vane machines, particularly compressors, liquid pumps, gas motors, `and internal combustion engines, steam engines, liquid motors and liquid-operated gears, and more particularly to such arrangements wherein the casing capsule ring radially encloses the rotor between the corresponding side wall extension of the rotor, said casing capsule ring being mounted for limited axial movement and for rotational movement with respect to the center point of the casing capsule ring.

Rotary vane machines of the type contemplated by the invention have been used heretofore in which the vanes slide radially or almost radially upwardly and inwardly within radially disposed slots provided in the rotor. A rotor side wall is provided at either end of the rotor which extends radially outwardly of the rotor and axially limits the rotor `a-t the corresponding end thereof. The casing capsule ring is generally disposed to radially enclose the rotor such that the casing capsule ring is slidably and intimately disposed between the rotor side walls in abutment therewith. lIn this way, the vane cells or intervene spaces of the rotary Vane machine are defined by the rotor at their radially yinward ends, the casing capsule ring at their radially outward ends, the rotor side walls at their axial or lateral sides, and the vanes or blades at their radial sides. The volume of the cells or intervane spaces increases and decreases during rotation of the rotor with respect to the casing of the machine where the casing capsule ring is eccentrically positioned with respect to the rotor, i.e. when the axis of the casing capsule ring is spaced from and parallel to the axis off the rotor rather than coincident therewith.

Various rotary vane machines are suitably disclosed, for example, in U.S. Pia-tent No. 2,348,428 to Tucker as well as in Belgian Patent No. 524,5 60, British Patent No. 744,446, Japanese Patent No. 225,237 and German Patent No. 916,739, and No. 1,020,869 which relate `to my own inventions,

In the operation of rotary vane machines of lthe foregoing type, a certain degree of undesired friction between the casing capsule ring land the rotor side walls gene-rally develops. Attempts have been made to decrease this friction by swingably supporting the casing capsule ring in the machine whereby such capsule ring may displaceably vary in position in dependence upon slight displacement of the rotor `and side walls during operation. Such constructions, however, only partially overcome objectionable friction between the moving parts rand fall far short of achieving complete elimination of friction.

Even rotation of the machine parts in a path which deviates slightly from the normal circular path tends to develop local heating `and cause high friction to be generated in the narrow fitting between the casing capsule ring and the rotor side walls. This objectionable action has been realized in practice and proposals to overcome the same include swingably suspending the casing capsule ring, for instance, in `accordance with U.S. Patents No. 2,658,456, and No. 2,881,708, yand French Patents No. 995,700, and No. 1,059,098, and others.

While the aforementioned patents succeed somewhat in reducing friction during rotary vane machine operation, the constructions set forth do not aiford reduction in friction tothe fullest extent possible. Due to the increasing widespread use of rotary vane machines, it has become increasingly limportant to provide rotary vane machine constructions in which lall avoidable friction sources may be eliminated in order to improve the total efliciency of such machines to the highest extent possible in practice.

It is an object of the present invention to overcome the foregoing drawbacks and to provide a casing capsule ring 4arrangement for `a rotary vane machine of the foregoing type wherein the casing capsule ring is mounted on supopr-t means therefor for limited axial movement and for rotational movement with respect to the center point of the casing capsule ring, `and which can be inserted between the side walls of the rotor. As another object of the invention is that the casing capsule -ring can be divided for instance into two parts and inserted between the radially enlarged axial side walls of the rotor. The feature of this arrangement is that rotor and rotor axial side walls can be manufactured in one piece enforcing the strength of lthe rotor parts for higher pressure and the like.

It is another object of the present invention to reduce the friction generated between the casing capsule ring and rotary side walls as well as the friction generated in the bearings of the capsule ring so as to increase substantially the total eciency of these rotary Vane machines. Other and further objects lof the invention will become apparent from a study of the within specification land accompanying drawings in which,

FIG. l is a longitudinal sectional View taken along the line 1 1 of FIG. 2, of a rotary vane machine illustrating the constructional arrangement of the casing capsule ring in accordance with the invention,

FIG. 2 is la sectional view, taken along the line II-II of FIG. 1 illustrating further details of construction, and

FIG. 3 is -a further partial view in section taken along the line III-lll of FIG. 1 illustrating the axially displaceable connection between the casing capsule ring and the support means therefor.

FIG. 4 is `a view of one half the casing capsule ring 1 looking at the joint faces.

FIG. 5 is a sectional view taken along the line V--V of iFIG. 4 but shown with respect to broth halves of the casing capsule ring to illustrate the means for connecting said halves together.

In accordance with the present invention, it has been found that Ian efficient casing capsule ring arrangement may be provided for a rotary vane machine, having a rotor operatively provided with vanes rand capable of rotation within the casing of the machine, the rotor and vanes defining with the casing a plurality of cells or intervene spaces which increase and decrease in volume during the rotation of the rotor and vanes, wherein friction generated by the moving parts sliding against one another will be decreased to a minimum. The casing capsule ring, Iin accordance with the invention, radially outwardly encloses at least a portion of the rotor and defines with the rotor and `the vanes, yas well as with the -side walls of the rotor a plurality of vane cells `or intervane spaces which increase and decrease in volume dur-ing the rotation of the rotor land vanes, the casing capsule ring being mounted on 'support means therefor, which permit limited axial movement as well as rotational movement with respect to the center point of the casing capsule ring.

Specifically, the casing capsule ring has a spherical outer surface and the support means includes-a spacing ring enclosing the casing capsule ring. The spacing ring is provided with a corresponding spherical inner surface for slidingly supporting the casing capsule ring therewithin. Preferably, the spherical surfaces of the casing capsule 3 ring and the spacing `ring have a constant radius of curvature. The spacing ring is advantageously provided as a bisected ring composed of two curved portions which are supported within and enclosed by a support ring.

The radially inner casing capsule ring, the intermediate bisected spacing ring, and the radially outer support 4ring are connected for common rotation by a pin which extends from the support ring through the spacing ring to the casing capsule ring. The pin is fixedly connected to the casing capsule ring and is axially displaceably connected to the spacing ring or bisected ring and the support ring. In this manner, while the casing capsule ring, the intermediate bisected ring and the support ring are mounted for common rotation, wherein the pin prevents relative rotational displacement between these parts, axial displacement of the casing capsule ring, and the bisected or spacing ring is possible to a limited extent with respect to each other and the support ring.

In particular, the pin is provided with a head block either integral therewith or separately formed having axial sliding surfaces. In the same way, the support ring is provided with corresponding axial sliding surfaces for coacting with the sliding surfaces of the head block. `In this manner, limited axial displacement of the pin is, therefore, permitted by means of the sliding coaction between the corresponding sliding surfaces. Of course, the pin is axially displaced, together with the casing capsule ring with which it is fixedly connected. Accordingly, the casing capsule ring may execute axial displacement due to -axial displacement of the rotor side walls in sliding abutment therewith, in consequence of which friction between the moving parts will be held at a minimum.

In this connection, the casing capsule ring is provided on each side lwith a radially outwardly extending lateral flange. These flanges are axially spaced from and connected to the casing capsule ring at their radially inward ends. The outermost radius of the lateral flanges is preferably greater than the radius of the spherical outer surface of the casing capsule ring whereby the corresponding bisected or spacing ring will be retained between said lateral flanges. As the aim of maximum strength and the capacity of highest pressure shall be reached according to another performance of this invention a rotor is with the innermost side walls as one piece, the casing capsule ring being divided into at least two parts in order to be fitted between the rotor side walls and to be rejoined again after assembly.

In order to execute the eccentric position of the support ring and in turn of the casing capsule ring with respect to the rotor axis, the support ring is mounted in a guide ring. The guide ring itself is mounted for radial displacement with respect to the rotor axis even during rotation of the support ring, bisected ring, and casing capsule ring.

The support ring is provided at its ends with radially inwardly disposed brace flanges and the guide ring is similarly provided at its ends with correspondingly radially inwardly disposed brace flanges. The brace flanges of the guide ring are axially outwardly positioned with respect to the support ring brace flanges. The support ring brace flanges and the guide ring brace fianges are interconnected at their correspondingly adjacent radially in ward ends by bearing means. Advantageously, by means of the brace flanges, the corresponding support and guide rings are secured against both axial and radial displacement with respect to the bearing means.

The bearing means may include any conventional arrangement. Preferably, circular Ibearing -means disposed between the adjacent 4brace fianges of the support and guide rings are used, such as roller bearings or ball bearings.

In order to further minimize frictional losses, the casing capsule ring and the spacing or bisected ring are provided with balancing pressure recess means dened in at least a portion of their surfaces. In the usual way, by providing a suitable pressure medium in such recess means,

excessive pressures exerted between abutting sliding surfaces of the casing capsule ring, the spacing ring, and adjacently disposed abutting sliding surfaces of other parts, will .be counteracted. In the same Way, lubricating recesses may be defined in the surfaces of the casing capsule ring and the `spacing ring. `By providing a lubricating medium in these recesses, effective lubrication of abutting sliding surfaces may be obtained.

Preferably, while the casing capsule ring is mounted so that it may rotate about its center point and execute limited axial movement as well as rotational movement, the support ring is so journaled to the ball bearings or roller bearings at the brace flange portion that the friction which may occur at this portion of the machine is effectively minimized. In this connection, in dependence upon the particular construction of the rotor, the brace anges are inwardly extended as far as is practical so that the bearing connection between adjacent brace flanges will define a circle of minimal diameter, Naturally, the corresponding circumference about which the ball bearings or roller bearings will be disposed will be correspondingly reduced to a minimum. Thus, the relative velocity between the bearings will be minimized such that the normally heavy friction `generated at the bearings will be avoided.

While, in the smaller rotary vane machine constructions heretofore known, an effective means for reducing friction along the capsule ring has been to journal the capsule ring by using `ball lbearings or roller bearings, friction is nevertheless bound to amount to about 3-6% of the total capacity wherein a steady rotational axis is considered. Where higher capacity rotary vane machines are contemplated, however, a loss in efiiciency of 3-6% becomes entirely too large for efficient operations. Generally, locomotive gears and engines as well as rotary vane machines used in ships must operate in this regard with a total efficiency of at least 96% in order to function efficiently and economically. Therefore, a loss in efficiency of more than 3% due to friction generated between the rotor side walls and the capsule ring as well as the friction generated at the ball bearings or roller bearings, can no longer be disregarded yand for practical industrial operations, the efficiency loss must be reduced to a value far below 3%.

The casing capsule ring arrangement in accordance with the invention achieves the high eciency desired and the ball bearing and roller bearing friction generated in this regard is decreased to about 1-l.5% of the total capacity of the machine. In the same way, the loss of friction, due to the casing capsule ring slidintgly engaging the rotor side walls is reduced to less than 0.5% of the total capacity of the machine, if, in addition, the blades or vanes are maintained in suitable balance. This loss in friction from these sources may be even further reduced to below 1.5% of the total capacity of the machine in accordance with the construction of the present invention. In this manner, machines of the rotary vane type using the instant casing capsule ring arrangement will operate at high eiciency, will meet the durability and toughest requirements sought in industrial practice, and will operate safely over an extended useful life.

IReferring to the drawings, casing capsule ring 1, having a spherical outer surface 27 and lateral flanges 29, is enclosed within split ring 2 in this instance made in two pieces, having a correspondingly spherical inner surface. In case the rotor 14 and its innermost side walls 18 are made in one piece, the casing capsule ring is divided into two or more parts 1a and 1b as per FIG. 4 and 5. After the assembly of the casing capsule ring 1 between the rotor side walls and connecting 1a and 1b in surface contacts 34a, these parts can be joined together by bolts 35 and nuts 36 and/ or centered by additional pins (passbolts) 37. In other cases it will be possible to center and support the casing capsule ring pieces 1a and 1b by rotor side walls 18 and bisected ring 2 without bolting. Bisected ring 2 is, in turn, enclosed within Isupport ring 7. A pin 3, provided with a head block 4 connects casing capsule ring 1, bisected ring 2 and support ring 7 for simultaneous rotation, pin 3 preventing relat-ive rotational displacement of these parts. Head block 4 contains a radially outwardly directed recess 4 in which the head of pin 3 is situated. Support ring 7 is provided with an opening containing guide surfaces 3l) and end openings 5 within which head block 4 is received in sliding engagement in axial direction. A cover ring 33 is suitably disposed on support ring 7 for retaining pin 35` and block 4 in the desired position. A space v6 is provided on either side of bisected ring Z whereby axial displacement of casing capsule ring 1 with respect to biseoted ring 2 may be carried out while pin 3 and head block 4 may be axially displaced, together with casing capsule ring 1 with respect to support ring 7. Since the lateral flanges 29 of casing capsule ring `1 extend radially outwardly with respect to spherical surface 27 and therefore of the corresponding spherical surface of bisected ring 2, bisected ring 2 will be laterally retained within anges 29.

The rotary vane machine generally includes an outer casing 111 within which is mounted at one end driving shaft 13 which is coupled to a suitable driving source (not shown) and a control shaft 20 at the other end. Drive shaft 13 and outer casing l11 are suitably provided with ball bearings 12 for reducing the friction generated during rotation to a minimum. Rotor 14 is provided with lateral side wall members 1=8 and 1.19, rotor :14 and rotor Side walls 1'8 and 19, being mounted on driving shaft 13 for rotation therewith. A bushing 3-4 is inserted between the radially inward adjacent surfaces of rotor 14 and rotor walls .18 and 19, in order that bushing 34 and rotor 14 rotate together on control shaft 20.

As may be seen from FIGURES l and 2, lluid may be passed to and from the vane cells or intervane spaces 25 via inlet and outlet passages Z1 and 22 defined in control shaft 20 as well as rotor passages 23 and 24.

The various cells or intervane spaces 2S are defined between rotor 14 on their radially inward side, rotor side walls 18 and 19 on their axial sides, casing capsule ring 1 on their radial outward sides and vanes =17 (see FIG. 2) on their rad-iai sides. Cells or intervane spaces 25 increase and decrease in volume las vanes 17 reciprocate within their respective recesses during the rotational travel of rotor 14 within casing capsule ring 1, due to the eccentric positioning of capsule ring 1 with respect to the axis of rotor 14.

Support ring 7 is provided with radially inwardly directed brace flanges 8 and 31 which are journaled with corresponding brace anges of guide ring to prevent the axial and radial displacement of support ring 7. The journal between support ring 7 and guide ring 10 is effected by means yof ball bearings 9 placed therebetween. A retaining ring 32 is inserted at one end of support rinlg 7 adjacent brace flange 8 `to prevent axial displacement of support ring 7. Y

As may be specically seen from FIGURE 2, channels 28 are defined between respective halves of bisected ring 2 which is inserted between casing capsule ring 1 and support ring 7. Bisected ring 2 is a spacing ring and is retained by the enclosing presence of support ring 7 as well `as by the retaining presence of pin 3 in connection with casing capsule ring v1. A plurality of conventional balancing pressure medium recesses 26 are provided in the sliding surfaces of casing capsule ring 1 and bisected ling 2, preferably on the outer surfaces thereof, in order to counteract excessive pressures aga-inst these parts. In this connection, in the usual way pressure medium is disposed within recesses 26, these recesses in each ring preferably being in common connection. Alternatively, a lubricating medium may be disposed within recesses 26 in order to effect fthe lubrication of the sliding parts.

lf the forces acting by Ifluid or gas under pressure work radially in the recesses 26 against the casing capsule ring pieces la and 1b the latter are tightly pressed together without any bolts, nuts, pins or the like. EIn operation, fluid may be passed to and from the cells 2S by means of inlet and outlet conduits Z1 and 2-2 and rotor conduits 23 and 24. Since driving shaft 13 is journaled in ball bearings 12 at one end or" outer casing =11 land rotor side Wall 11-9 and its corresponding axial extension is journaled in bearings 12 at the other end of casing 11, the unit, including side walls '1S and 19, rotor 14, and shaft 1.3 will revolve together about the control shaft 20. As this turning takes place, inlet and outlet conduits 21 and 22 will be alternately in communication with the various cells 25 as rotor conduits 23 and 24 revolve. Guide ring 10 is mounted in outer casing 11 for axial displacement with respect to the axis of rotor `14. Since support ring 7 is journaled for rotation with respect to guide ring 10, which does not rotate, such journal-ing being provided at both ends by bal-l bearings 9, support ring 7, and in turn, bisected ring 2 and capsule ring 1 will rotate with respect to guide ring `1i).

rThus, shaft 13 and, in turn, side walls 18 and 19 will rotate in the same direction as that of casing capsule ring 1, bisected ring 2 and support ring 7. Actually, the sliding abutment between lateral flanges 29 of casing capsule ring 1 and side walls 18 and 19 of rotor 14 will cause casing capsule ring 1 to rotate somewhat therewith. Nevertheless, since guide ring 1li, which does not rotate, may be axially displaced with respect to the axis of rotor 14, casing capsule ring 1, in turn, will be axially displaced so that this ring will be eccentrically positioned with respect to rotor 14. in this manner, as the rotation is carried out cells 25 of increasing and decreasing volume will be formed, for example, in the case where the rotary Vane machine is used as a pump, such that during the increasing volume portion of a cycle, fluid will be drawn into cells 2S and thereafter forced out of these cells during the next half cycle of decreasing volume.

In accordance with the construction of the invention, the journal 9 is provided at a radius as small as practicable so as to avoid undue friction which might be generated at a greater circumference. Due to the mounting of casing capsule ring 1, this ring may slide, together with the rotor side walls 1S and 19, to minimize the friction between these moving parts. Moreover, since casing capsule ring 1 may be axially displaced due to the provision for mounting head block 4 within openings 5 of support ring 7, utilizing the guiding surface 35, changes in the axial positioning of rotor 14 and side walls 18 and 19 will merely cause a corresponding axial change in the position of casing capsule ring 1 without generating undue friction or stress on either lateral flange 29. Thus, the spherical mounting of capsule ring 1 in bisected spacing ring 2 will permit the rotational movement of casing capsule ring 1 about its center point to a limited extent while overall rotational movement of casing capsule ring 1 with respect to its center point will be achieved due to the journaled connections at ball bearings 9.

lt will be appreciated that most effective minimizing of friction will be afforded if the spherical inner surface of bisected ring 2 and the spherical outer surface of casing capsule ring 1 have a constant radius of curvature around the center point of casing capsule ring 1. It will be appreciated in this connection that the casing capsule ring 1 may rotate in both directions around its center point with its spherical outer surface 27 maintained within the corresponding spherical inner surface of bisected ring 2, whereby capsule ring 1 may swing or pivot to compensate any errors in the rotational path of rotor 14 and, in turn, rotor side Walls 13 and 19 with respect to capsule ring 1. Generally, between the outer surface of bisected ring 2 and the inner surface of support ring 7, a slight clearance is maintained so that bisected ring 2 may move axially within support ring 7 corresponding to axial movements and errors or variations in the rotational path of rotor 14 and rotor side walls 1S and 19. By preferably providing the radius of curvature of spherical surface 27 less than the radially outward ends of anges 29, a saving in space is achieved and bisected ring 2 will be disposed so that it cannot slip olf into the lateral grooves within flanges 29 of capsule ring 1. It will be appreciated that a slight axial clearance is provided between pin 3 and bisected ring 2 so that bisected ring 2 may axially vary with respect to pin 3 and the parts connected thereto.

Nevertheless, in order to prevent relative rotational motion between casing capsule ring 1, bisected ring 2, and support ring 7, as for example, where the rotation of capsule ring 1 is started, accelerated or reduced in rate in dependence upon the inertia of support ring 7, bisected ring 2 or brace flange 8, for example, these members are maintained in xed rotational relation by means of pin 3 and block 4.

The high efficiency of the construction in accordance with the invention of rotary vane machines, preferably includes maintaining the radius of bearings 9 as small as possible and generally smaller than the corresponding radius of casing capsule ring 1. To obtain greater supporting capacity, larger size ball or roller bearings 9 may be used or double row type ball or roller bearings may be provided in axial direction. The further efiiciency and reduction in friction is achieved by the particular mounting of casing capsule ring 1, such that it may execute limited rotational movement with respect to its center point, i.e. in a plane passing axially through its center point as well as rotational movement about the axis of rotor 14 and axial displacement along the axis of rotor 14.

What is claimed is:

1. Rotary vane machine which comprises a casing, a rotor within the casing, vanes mounted on said rotor for movement in an outward direction, a rotatable capsule ring having an inner cylindrical surface forming a pumping chamber, said capsule ring encircling and radially enclosing at least a portion of said rotor eccentrically with respect to said cylindrical surface and defining therewith and with said vanes a plurality of intervane spaces which increase and decrease in volume during rotation of said rotor, inlet and outlet means communicating with said pumping chamber, a support for said capsule ring rotatable together therewith, and intermediate spacing and interconnector means cooperative with said capsule ring and said support and rotatable therewith to permit limited but substantially free relative movement between said capsule ring and said support in axial direction and in a direction transverse to a radial plane through the axis of said capsule ring.

2. Machine according to claim l wherein said capsule ring has a spherical outer surface and said intermediate spacing means includes a spacing ring enclosing said cap` sule ring, said spacing ring having a corresponding spheric al inner surface for slidingly supporting said capsule rlng.

3. Machine according to claim 2 wherein said spacing ring is spherically slidable on said capsule ring and radially outwardly encircled by said support, a pin being xedly disposed at one of its ends in said capsule ring and extending therefrom radially outwardly through said spacing ring and having its other radially outer end extending into said support with clearance therebetween axially of the rotor to provide freedom of axial and tilting movement of said capsule ring with respect to said support.

4. Machine according to claim 3 wherein said spacing ring includes at least two separate curved spacing ring elements between said capsule ring and said support.

5. Machine according to claim 4 wherein said pin at its radially outer end is disposed lixedly in a head block having an axial sliding surface and said support has a corresponding axial sliding surface coacting with the sliding surface of said head block for permitting limited axial displacement of said pin by sliding coaction between said sliding surfaces.

6. Machine according to claim 5 wherein said capsule ring is provided on each side with a radially outwardly extending lateral flange `axially spaced from one other and connected to said capsule ring at their respective radially inward ends by an axially extending portion disposed therebetween, the outermost radius of the flanges being greater than the radius :of the spherical outer surface of said capsule ring.

7. Machine according to claim 6 wherein said support is in the form of a support ring, and wherein said support ring, said spacing ring and said capsule ring are further rotatably mounted within lan encircling guide support displaceable in a direction transverse to the axis of the rotor for radial displacement with respect to a given axis of said support ring, of said spacing ring and of said capsule ring even during rotation of said rings and said rotor.

8. Machine according to claim 3 wherein said support tis in the form of a support ring, and wherein said capsule ring and said spacing ring lare provided with pressure medium retaining recesses defined in at least a portion of their respective sliding surfaces to receive pressure medium for counteracting excessive pressures exerted between abutting sliding surfaces of said capsule ring and said spacing ring and ladjacently disposed abutting sliding surfaces of said support ring.

9. Machine according to claim 3 wherein said support is in the form of a support ring, and wherein said capsule ring and spacing ring are provided with lubricating medium retaining recesses defined in at least a portion of their respective sliding surfaces -to receive lubricating medium for lubricating abutting sliding surfaces of said capsule ring and said spacing ring Iand :adjacently disposed abutting sliding surfaces of said support ring.

10. Machine [according to claim 2 wherein said support is further outwardly rotatably mounted within a rotationally stationary and radially displaceable encircling guide support for simultaneous radial displacement, with respect to the rotor axis, of said support, spacing ring and capsule ring.

11. A machine as set forth in claim 1 in which said rotor is provided with side walls extending radially to enclose said vanes laterally.

12. Machine `according `to claim 11 wherein said capsule ring is split substantially radially into more than one separate capsule ring portion in order to be fitted between the innermost side walls ofthe rotor.

13. Rotary vane machine which comprises a casing. a rotor mounted in said casing, vanes mounted in slots of said rotor for movement periodically substantially radially inwardly and outwardly in said slots during rotation of said rotor, a rotatable capsule ring encircling and radially enclosing at least a portion of said rotor, said capsule ring having an inner face and being mounted eccentrically adjustably with respect to .the 'axis of said rotor, said rotor having axial end portions extending axially in both directions, said axial end portions each being provided with a rotor side wall, said rotor side walls extending radially outwardly beyond said inner face of said capsule ring, said rotor side walls being provided with radial plane medial faces, said capsule ring being provided with radial plane end faces with said plane end faces being at least radially slidably disposed between said medial faces, said rotor, said vanes, said rotor side walls, Iand said inner face of said capsule ring together defining a plurality of intervane spaces which increase and decrease in volume during rotation of said rotor, said capsule ring being provided with an outer bearing surface forming at least a part of the radially outer periphery thereof, support means rotatable with said capsule ring and having at least one radial bearing portion surrounding and bearing said capsule ring, said radial bearing portion being provided with at least one inner bearing face and said louter bearing portion of said capsule ring Ibeing slidably disposed in the said inner bearing face of said radial bearing portion.

14. Machine Vaccording to claim 13 wherein the said support means include a support ring carrying radially therewithin a spacing ning, said inner bearing face being provided on the inner surface of said spacing ning with said spacing ring carrying madially therewithiin said capsule ring, said capsule ring, spacing ring and suppomt ring being connected together `for simultaneous rotation and with limited but substantially free movement therebetween axially and rotationlally transverse to the taxis of said capsule ring.

15. Machine according to claim 13 wherein the capsule ring beaming pomtion is provided with a spherical outer face, said nadial bearing portion being a radially split ring inserted between said capsule ring bearing portion and said support ning, said split ring having Aa cylindrical outer face and a spherical inner face, said spherical inner face corresponding to said spherical outer face ci said capsule ring bearing portion, said cylindrical outer face being slidably fit-ted within said cylindrical inner face.

References Cited in the file of this patent UNITED STATES PATENTS 1,460,487 Hawkins July 3, 1923 1,965,388 Oh July 3, 1934 2,087,816 Saussard et al July 20, 1937 2,289,866 Benedek July 14, 1942 2,348,428 Tucker May 9, 1944 y2,558,837 Frei July 3, 1951 2,681,621 Hedman June 22, 1954 2,750,895 Sturm June y19, 1956 2,791,184 Sturm May 7, 1957 2,918,877 Woodcock Dec. 29, 1959 2,961,969 Vanderstegen-Drake Nov. 29, 1960 3,011,449 Ernst Dec. 5, 1961 FOREIGN PATENTS 1,232,183 France Apr. 19, 1960 

1. ROTARY VANE MACHINE WHICH COMPRISES A CASING, A ROTOR WITHIN THE CASING, VANES MOUNTED ON SAID ROTOR FOR RING HAVING AN OUTWARD DIRECTION, A ROTATABLE CAPSULE RING HAVING AN INNER CYLINDRICAL SURFACE FORMING A PUMPING CHAMBER, SAID CAPSULE RING ENCIRLING AND RADIALLY ENCLOSING AT LEAST A PORTION OF SAID ROTOR ECCENRICALLY WITH RESPECT TO SAID CYLINDRICAL SURFACE AND DEFINING THEREWITH AND WITH SAID VANES A PLURALITY OF INTERVANE SPACES WHICH INCREASE AND DECREASE IN VOLUME DURING ROTATION OF SAID ROTOR, INLET AND OUTLET MEANS COMMUNICATING WITH SAID PUMPING CHAMBER, A SUPPORT FOR SAID CAPSULE RING ROTATABLE TOGETHER THEREWITH, AND INTERMEDIATE SPACING AND INTERCONNECTOR MEANS COOPERATIVE WITH SAID CAPSULE 